CN112681994A - Low-pressure-consumption high-amplitude hydraulic pulse device and method - Google Patents
Low-pressure-consumption high-amplitude hydraulic pulse device and method Download PDFInfo
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- CN112681994A CN112681994A CN202110303052.6A CN202110303052A CN112681994A CN 112681994 A CN112681994 A CN 112681994A CN 202110303052 A CN202110303052 A CN 202110303052A CN 112681994 A CN112681994 A CN 112681994A
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Abstract
The invention provides a low-pressure-consumption high-amplitude hydraulic pulse device and a method, and solves the technical problem that the hydraulic pulse amplitude of a hydraulic pulse device in the prior art is small. The valve comprises an outer shell (10), a fixed valve seat (20) and a movable valve (30); the shell inner cavity is arranged in the shell (10); a discharge port (11) is arranged on the outer shell (10); the fixed valve seat (20) is fixed in the inner cavity of the shell; a valve seat inner cavity is arranged inside the fixed valve seat (20); the fixed valve seat (20) is provided with a throttling port (21), a bypass port (22) and a flow channel (23); a valve (30) is slidably connected in the housing interior and the valve seat interior. The invention combines the advantages of the hydraulic positive pulse device and the hydraulic negative pulse device, the hydraulic pulse amplitude is larger, the pressure wave is spread farther along the interior of the pipe column, the vibration length of the drill column is longer, and the friction force between the pipe column and the well wall is smaller.
Description
Technical Field
The invention relates to the field of pulse generation, in particular to a low-pressure-consumption high-amplitude hydraulic pulse device and method.
Background
Along with the increasing difficulty in mining resources such as petroleum, natural gas, geothermal heat, ground ore and the like, more and more directional wells, long horizontal wells and extended reach wells are provided, and the friction resistance between a pipe column and a well wall is large, so that the decompression of a drill bit is serious in the drilling process, and the drilling efficiency is low.
In order to solve the problem of large frictional resistance between the pipe column and the well wall, a water pulse device is usually added in the drill column, and the static friction between the pipe column and the well wall is converted into dynamic friction through the axial vibration generated by the water pulse device, so that the frictional resistance between the pipe column and the well wall is reduced. Two types of current commercialized hydraulic pulse devices, one type is an NOV hydraulic oscillator, the flow area is changed through a stator and rotor driving mode to generate pulse pressure, when the flow area is reduced, the pressure at the upstream of a valve is increased, and when the flow area is increased, the pressure at the upstream of the valve returns to normal pressure, the hydraulic pulse device can increase the pressure consumption of a drilling circulation by 4-5 MPa, but in a well team with poor pump manifold conditions, the traditional hydraulic pulse device cannot be used due to the difficulty in providing high pump pressure; the other type is a negative pulse hydraulic oscillator of CT energy, which releases pressure of fluid in a pipe column through the periodic opening of a discharge channel so as to generate periodic hydraulic pulses, and the maximum advantage of the hydraulic pulse device is that the circulating pressure consumption of a well is not additionally increased, but the amplitude of the hydraulic pulses generated by the hydraulic pulse device is influenced by the pressure consumption of a lower tool string, and if the pressure consumption of the lower tool string of the hydraulic pulse device is smaller, the amplitude of the generated hydraulic pulses is also very small. However, the amplitude of the generated hydraulic pulse is smaller in the current two types of hydraulic pulse devices.
Disclosure of Invention
The invention aims to provide a low-pressure-consumption high-amplitude hydraulic pulse device to solve the technical problem that the hydraulic pulse amplitude of a hydraulic pulse device in the prior art is small. The technical effects that can be produced by the preferred technical scheme in the technical schemes provided by the invention are described in detail in the following.
In order to achieve the purpose, the invention provides the following technical scheme:
a low-pressure-consumption high-amplitude hydraulic pulse device comprises an outer shell, a fixed valve seat and a movable valve; a shell inner cavity is arranged in the outer shell; a drainage port is arranged on the outer shell; the fixed valve seat is fixed in the inner cavity of the shell; a valve seat inner cavity is arranged inside the fixed valve seat; the lower part of the fixed valve seat is provided with a throttling opening and a flow passage; the fixed valve seat is also provided with a bypass port; the movable valve is connected in the inner cavity of the shell and the inner cavity of the valve seat in a sliding manner; the movable valve is provided with a movable valve drain port and a movable valve bypass port; and a central flow passage is arranged in the center of the movable valve.
The axes of the outer shell, the fixed valve seat and the movable valve are overlapped.
The movable valve does axial reciprocating motion along the axis direction; the movable valve reciprocates circumferentially about an axis.
The outer shell is provided with at least one drainage port; the bleed port may be a circular hole or other shaped passage.
The fixed valve seat is provided with at least one bypass port; the bypass port may be a circular hole or other shaped passage.
The movable valve is provided with at least one movable valve drainage port; the valve port can be a circular hole or other shaped passage.
The movable valve is provided with at least one movable valve bypass port; the valve bypass port may be a circular hole or other shaped passage.
The movable valve drain port and the drain port form a drain channel; the valve bypass port and the bypass port form a bypass passage.
The invention can at least produce the following technical effects:
the invention combines the advantages of the hydraulic positive pulse device and the hydraulic negative pulse device to generate larger hydraulic pulse amplitude, so that pressure waves are further transmitted along the interior of the pipe column, the vibration length of the pipe column is longer, and the friction force between the pipe column and the well wall is smaller.
Drawings
FIG. 1 is a schematic block diagram of a first position in accordance with an embodiment of the present invention;
FIG. 2 is a schematic structural view of a second position of the embodiment of the present invention;
FIG. 3 is a schematic diagram of a third position in accordance with an embodiment of the present invention;
FIG. 4 is a schematic diagram of a fourth position in accordance with the present invention;
FIG. 5 is a graph of a pressure waveform generated by an embodiment of the present invention;
FIG. 6 is a schematic structural diagram of a closed state according to an embodiment of the present invention;
FIG. 7 is a cross-sectional view A-A of FIG. 6;
FIG. 8 is a cross-sectional view B-B of FIG. 6;
FIG. 9 is a schematic structural diagram illustrating an open state according to an embodiment of the present invention;
FIG. 10 is a cross-sectional view A-A of FIG. 9;
fig. 11 is a sectional view of B-B in fig. 9.
In the figure: 10-an outer shell; 11-a drain port; 12-a bypass flow channel; 13-an outlet flow channel; 20-fixed valve seat; 21-a choke; 22-a bypass port; 23-a flow channel; 30-a valve; 31-a valve bleed port; 32-a valve bypass port; 33-center flow channel.
Detailed Description
As shown in fig. 1, a low-pressure consumption high-amplitude hydraulic pulse device comprises an outer shell 10, a fixed valve seat 20 and a movable valve 30; a shell inner cavity is arranged inside the outer shell 10; a discharge port 11 is arranged on the outer shell 10; the fixed valve seat 20 is fixed in the inner cavity of the shell, and a bypass flow passage 12 is formed between the fixed valve seat 20 and the outer shell 10; a valve seat inner cavity is arranged inside the fixed valve seat 20; the lower part of the fixed valve seat 20 is provided with a throttling orifice 21 and a flow passage 23, the flow area of the throttling orifice 21 is far smaller than that of the central flow passage 33, and a throttling effect is formed; the fixed valve seat 20 is also provided with a bypass port 22; the movable valve 30 is connected in the inner cavity of the shell and the inner cavity of the valve seat in a sliding mode; the movable valve 30 is provided with a movable valve leakage port 31 and a movable valve bypass port 32; the valve 30 has a central flow passage 33 in the center.
As an alternative embodiment, the axes of the outer housing 10, the fixed valve seat 20 and the movable valve 30 are coincident, so that the movable valve 30 can reciprocate axially and circumferentially in the outer housing 10 and the fixed valve seat 20.
As an alternative embodiment, the valve 30 reciprocates axially in the axial direction; the valve 30 reciprocates circumferentially about an axis.
As an optional embodiment, at least one drainage port 11 is provided on the outer shell 10; the bleed port 11 may be a circular hole or other shaped passage.
As an alternative embodiment, the fixed valve seat 20 is provided with at least one bypass port 22; the bypass port 22 may be a circular hole or other shaped passage.
As an alternative embodiment, the valve 30 is provided with at least one valve bleed port 31; the valve bleed port 31 may be a circular hole or other shaped passage.
In an alternative embodiment, the valve 30 is provided with at least one valve bypass port 32; the valve bypass port 32 may be a circular hole or other shaped passage.
As an alternative embodiment, the valve outlet port 31 and the outlet port 11 form a vent path; the valve bypass port 32 and the bypass port 22 form a bypass passage; the valve 30 moves relative to the outer housing 10 and the stationary seat 20 to periodically open and close the drain and bypass passages.
As an alternative, the pressure measuring element may be a pressure sensor.
The working process of the invention is as follows:
when the movable valve 30 only does axial reciprocating motion along the axial direction, the invention has four critical point positions, the first position is shown in fig. 1, at this time, the movable valve 30 moves to the lowest end position, the drain passage is all opened, and the bypass passage is all opened; a second position, as shown in FIG. 2, in which the drain passage is about to begin to close and the bypass passage is about to begin to close; the third position is as shown in fig. 3, the closing of the bleed passage is completed, and the closing of the bypass flow is completed; fourth position As shown in FIG. 4, the valve 30 has moved to an uppermost position, the vent path is fully closed, and the bypass flow path is fully closed.
The valve 30 moves upwardly to its uppermost position from the third position to the fourth position, during which time the valve 30 moves a distance L2 and the vent and bypass passages are fully closed; the valve 30 moves downward from the fourth position to the third position, during which the valve 30 moves a distance L2 and the vent path and the bypass path are completely closed; in the two processes, all the fluid flows out of the hydraulic pulse device through the central flow passage 33, the throttling orifice 21 and the outlet flow passage 13 in sequence, and the fluid at the upper part of the hydraulic pulse device is high pressure due to the throttling effect of the throttling orifice 21, and a horizontal wave peak section as shown in fig. 5 is generated as the fluid is measured by the pressure measuring piece.
The valve 30 continues to move downwardly from the third position to the second position, during which the vent and bypass passages are progressively opened until fully opened, a portion of the fluid is discharged through the vent passage, a portion of the fluid flows through the hydraulic pulse device through the bypass flow passage, and the pressure measurement reveals that during this process the pressure at the upper portion of the hydraulic pulse device is rapidly reduced, creating a downwardly sloping segment as shown in fig. 5.
The valve 30 continues to move downwardly to its lowermost end from the second position to the first position with the vent and bypass passages fully open for a distance L1; the valve 30 moves upward from the first position to the second position with the vent and bypass passages fully open for a distance L1. At this time, a part of the fluid flows into the outside of the hydraulic pulse device through the valve discharge port 31 and the discharge port 11, and the pressure outside the hydraulic pulse device is much lower than that of the central flow passage 33; one part of the fluid flows through the bypass port 32 of the movable valve, the bypass port 22, the bypass flow channel 12 and the flow channel 23, and one part of the fluid flows through the throttling port 21 and is merged in the outlet flow channel 13 to flow out of the hydraulic pulse device, and the pressure measuring part detects that the fluid at the upper part of the hydraulic pulse device is low pressure, so that a horizontal wave valley section shown in fig. 5 is generated.
The valve 30 continues to move upward from the second position to the third position, during which the vent and bypass passages progressively close until fully closed, and as the flow areas of the vent and bypass passages decrease, the pressure sensing member measures that the fluid pressure in the upper portion of the hydraulic pulse device progressively increases, creating an upwardly sloping line segment as shown in fig. 5.
The above-described processes form a complete cycle, resulting in a rectangular-like hydraulic pulse waveform as shown in fig. 5. The hydraulic pulse device produces a pressure amplitude that is much greater than that which would be produced by opening and closing only the bleed passage, or only the bypass passage. In addition, the distance ratio of L1 and L2 can be controlled to control the widths of the wave crest and the wave trough in the rectangular hydraulic pulse, and when the opening length L1 is greater than the closing length L2, the pressure consumption of the hydraulic pulse device is lower under the condition of generating the same pressure amplitude.
The present invention has two states, closed and open, when the valve 30 is reciprocated circumferentially about the axis. In the closed state shown in fig. 6-8, with both the drain and bypass passages closed, fluid exits the hydraulic pulse device through the center flow passage 33, the restriction 21, and the outlet flow passage 13 in that order.
In the open state shown in fig. 9-11, both the drain passage and the bypass passage are open; a portion of the fluid exits through the valve outlet port 31 and the outlet port 11, where the pressure outside the hydraulic pulse device is much lower than the pressure in the center flow passage 33; a portion of the fluid passes through the restriction 21 and joins the outlet flow channel 13 to exit the hydraulic pulse device.
The valve 30 rotates clockwise, so that the hydraulic pulse device is switched from a closed state to an open state, the drainage channel and the bypass channel are opened simultaneously, and the pressure at the upper part of the hydraulic pulse device is suddenly reduced as measured by the pressure measuring piece as a result of the sudden increase of the flow area of a part of fluid which is discharged through the drainage channel and flows downwards through the hydraulic pulse device; then the valve 30 continues to rotate clockwise, the drainage channel and the bypass channel are kept in an open state, and the pressure measuring part measures that the pressure at the upper part of the hydraulic pulse device is maintained in a low-pressure state; the valve 30 continues to rotate clockwise, so that the hydraulic pulse device is switched from an open state to a closed state, the drainage channel and the bypass channel are closed simultaneously, and the pressure measurement piece finds that the fluid pressure at the upper part of the hydraulic pulse device is increased due to the throttling effect of the throttling opening 21; the valve 30 then continues to rotate clockwise, the drain and bypass passages remain closed and the pressure gauge measures that the pressure in the upper portion of the hydraulic pulse bank remains high. With the rotational movement of the valve 30, the drain and bypass passages are periodically opened and closed, thereby creating periodic hydraulic pulses.
By the structure, the pressure amplitude generated by the hydraulic pulse device is much larger than that generated by only opening and closing the drainage channel or only opening and closing the bypass channel, so that the pressure wave is further propagated along the interior of the pipe string, the vibration length of the drill string is longer, and the friction force between the pipe string and the well wall is smaller.
The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present invention, and all the changes or substitutions should be covered within the scope of the present invention.
Claims (8)
1. A low-pressure-consumption high-amplitude hydraulic pulse device is characterized in that: comprises an outer shell (10), a fixed valve seat (20) and a movable valve (30); a shell inner cavity is arranged in the shell (10); a drainage port (11) is arranged on the outer shell (10); the fixed valve seat (20) is fixed in the inner cavity of the shell; a valve seat inner cavity is arranged in the fixed valve seat (20); the lower part of the fixed valve seat (20) is provided with a throttling opening (21) and a flow passage (23); a bypass opening (22) is also formed in the fixed valve seat (20); the movable valve (30) is connected in the inner cavity of the shell and the inner cavity of the valve seat in a sliding mode; the movable valve (30) is provided with a movable valve drainage port (31) and a movable valve bypass port (32); the center of the movable valve (30) is provided with a central flow passage (33).
2. The low-pressure-loss high-amplitude hydraulic pulse device according to claim 1, wherein: the axes of the outer shell (10), the fixed valve seat (20) and the movable valve (30) are overlapped.
3. The low-pressure-loss high-amplitude hydraulic pulse device according to claim 1, wherein: the outer shell (10) is provided with at least one drainage port (11).
4. The low-pressure-loss high-amplitude hydraulic pulse device according to claim 1, wherein: the fixed valve seat (20) is provided with at least one bypass opening (22).
5. The low-pressure-loss high-amplitude hydraulic pulse device according to claim 1, wherein: the valve (30) is provided with at least one valve bleed port (31).
6. The low-pressure-loss high-amplitude hydraulic pulse device according to claim 1, wherein: the valve (30) is provided with at least one valve bypass port (32).
7. The low-pressure-loss high-amplitude hydraulic pulse device according to claim 1, wherein: the movable valve drain port (31) and the drain port (11) form a drain channel; the valve bypass port (32) and the bypass port (22) form a bypass passage.
8. A method of pulse generation using a low-loss high-amplitude hydraulic pulse device as defined in any one of claims 1 to 7, wherein: the method comprises the following steps:
s1: the upper part of the movable valve (30) is provided with a pressure measuring piece for measuring the pressure on the upper part of the movable valve;
s2, making the valve (30) do axial reciprocating motion along the axial direction, which comprises the following steps:
s21: the movable valve (30) moves to the uppermost end of the low-pressure consumption high-amplitude hydraulic pulse device;
s21: the movable valve (30) moves downwards to the lowest end of the low-pressure-consumption high-amplitude hydraulic pulse device, and the drainage channel and the bypass channel are in a completely closed state, a gradually opened state and a completely opened state in sequence;
s22: the movable valve (30) moves upwards to the uppermost end of the low-pressure-consumption high-amplitude hydraulic pulse device, and the drainage channel and the bypass channel are in a completely opened state, a gradually closed state and a completely closed state in sequence;
s23: repeating steps S21 and S22;
s3: causing the valve (30) to reciprocate circumferentially about the axis, comprising the steps of:
s31: a rotary valve (30) for completely closing the drain passage and the bypass passage;
s32: the movable valve (30) rotates for a circle in a single direction, so that the drainage channel and the bypass channel are in a complete closing state, a gradual opening state, a complete opening state, a gradual closing state and a complete closing state in sequence.
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| CN202110303052.6A CN112681994B (en) | 2021-03-22 | 2021-03-22 | Low-pressure-consumption high-amplitude hydraulic pulse device and method |
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| CN112681994B (en) | 2021-07-13 |
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